EP0156553A1 - Balanced valve coupling - Google Patents
Balanced valve coupling Download PDFInfo
- Publication number
- EP0156553A1 EP0156553A1 EP85301538A EP85301538A EP0156553A1 EP 0156553 A1 EP0156553 A1 EP 0156553A1 EP 85301538 A EP85301538 A EP 85301538A EP 85301538 A EP85301538 A EP 85301538A EP 0156553 A1 EP0156553 A1 EP 0156553A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- coupling
- parts
- sleeve
- fluid
- valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
- F16L37/00—Couplings of the quick-acting type
- F16L37/28—Couplings of the quick-acting type with fluid cut-off means
- F16L37/30—Couplings of the quick-acting type with fluid cut-off means with fluid cut-off means in each of two pipe-end fittings
- F16L37/32—Couplings of the quick-acting type with fluid cut-off means with fluid cut-off means in each of two pipe-end fittings at least one of two lift valves being opened automatically when the coupling is applied
- F16L37/36—Couplings of the quick-acting type with fluid cut-off means with fluid cut-off means in each of two pipe-end fittings at least one of two lift valves being opened automatically when the coupling is applied with two lift valves being actuated to initiate the flow through the coupling after the two coupling parts are locked against withdrawal
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
- F16L37/00—Couplings of the quick-acting type
- F16L37/22—Couplings of the quick-acting type in which the connection is maintained by means of balls, rollers or helical springs under radial pressure between the parts
- F16L37/23—Couplings of the quick-acting type in which the connection is maintained by means of balls, rollers or helical springs under radial pressure between the parts by means of balls
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/87917—Flow path with serial valves and/or closures
- Y10T137/87925—Separable flow path section, valve or closure in each
- Y10T137/87965—Valve- or closure-operated by coupling motion
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/87917—Flow path with serial valves and/or closures
- Y10T137/87925—Separable flow path section, valve or closure in each
- Y10T137/87973—Coupling interlocked with valve, or closure or actuator
Definitions
- Couplings with self-sealing valves are commonly utilized in fluid circuits to prevent the escape of fluid when the parts are uncoupled.
- Such self-closing valves are usually spring biased, and are located within the coupling part adjacent the end thereof whereby the valves of the parts engage during coupling to displace each other and open the part passages.
- Such self-sealing couplings are easily connected if the fluid pressure within a part, or parts, is nil or low, but internal pressure renders coupling of self-sealing parts difficult if the internal fluid pressure must be overcome to displace the valves and permit complete interlocking of the parts.
- Fluid couplings used with agricultural equipment must be readily coupled and uncoupled, self-sealing, and of the "breakaway" type wherein the coupling parts automatically separate when the axial tension in the hose lines reaches a predetermined force, as will happen if the implement being towed by the tractor is inadvertently dehitched, or the hitch trips because the implement strikes an immovable object.
- Another object of the invention is to provide a fluid coupling wherein the interconnection of the coupling parts is achieved by a manually operated lever, and coupling of the parts is assisted by the hydraulic pressure within the pressurized supply circuit.
- a further object of the invention is to provide a self-sealing fluid coupling utilizing standard interfaces, and wherein interconnection of the parts is hydraulically assisted.
- Yet another object of the invention is to provide a "breakaway" self-sealing fluid coupling wherein the coupling parts each contain self-sealing-valves, and fluid pressure within the supply part is utilized to unseat the self-sealing valve within the supplied part permitting mating and interlocking of the coupling parts regardless of the fluid pressure within the supplied circuit.
- the female coupling part is connected to the supply side of the circuit utilizing a pump, while the male coupling part communicates with the supplied circuit.
- the coupling parts utilize standard interface configurations, and an annular sleeve mounted upon the female part utilizes radially movable balls to connect to the male part and a manually operated lever axially translates the sleeve to draw the male part into the female.
- An expansible chamber motor is defined in the female coupling part communicating with the supplied pressurized fluid during part interconnection to assist in the axial displacement of the sleeve and operation of the lever.
- the self-sealing valve within the female and male coupling parts engage during interconnection and the female part includes an expansible booster motor in communication with the supplied pressure for displacing the male self-sealing valve if the pressure within the supply circuit is too great to permit the self-sealing valve to open during mech.anical interconnection.
- This booster motor assures opening of the supplied circuit regardless of the static pressure therein.
- the sleeve may be displaced by the tension within the coupling parts to provide a "breakaway" operation, and the aforementioned structure is concisely incorporated within a coupling configuration and size comparable to available couplings for similar applications.
- the coupling female part 10 is usually hard mounted, such as being attached to the pressurized supply circuit of the tractor or the like.
- the supplied circuit such as the circuit of a farm implement, includes the male part 12 mounted upon a flexible hose 14 and connectable to the female part 10.
- the female part -10 includes a passage 16 internally threaded at the left to receive a pressurized conduit from the pump, having a tubular sleeve which telescopingly supports the valve 20 which is biased toward a sealing relationship with the conical seal 22 by compression spring 24.
- annular sleeve 26 is mounted upon the coupling part 10 for axial displacement, and the sleeve includes an annular piston head 28 internally and externally grooved to receive sealing rings 32.
- the annular cap 34 mounted upon the part 10 forms an annular chamber 36 in which the sleeve piston head 28 reciprocates.
- the sleeve 26 is provided with a cylindrical portion 38 having a plurality of radially extending circumferentially spaced holes each receiving a radially movable ball 40.
- a snap ring 42 defined in a groove adjacent the right end of the sleeve limits the movement of the annular ball retainer 44 on the sleeve 26 as biased to the right by the compression spring 46.
- the ball retainer 44 includes an annular recess 48 partially defined by an oblique cam surface, and movement of the retainer to the right is limited by engagement with the snap ring 42, or the snap ring 50 located within the annular cap 34.
- a flexible elastic skirt 52 prevents the entrance of foreign matter.
- An operating shaft 54 is rotatably mounted upon the cap 34 within cylindrical recess 56, and the shaft includes a handle 58 pinned thereto. At its lower portion the shaft includes an eccentric pin 60 received within the annular groove 62 defined within the sleeve 26 whereby rotation of the shaft by the handle 58 will axially displace the sleeve upon the coupling part 10.
- Spring detent means may be utilized to hold the shaft 54 in its open and closed rotary positions upon the cap 34.
- a booster piston assembly generally indicated at 64 is located within the passage of the female part 10, and the booster piston includes a head 66 sealingly engaging the sleeve by means of an O-ring.
- the booster piston 64 includes an axially extending portion 68 also sealed to the sleeve and a central valve 70 is defined in the booster piston engagable with seat 74.
- the valve 70 is biased to the right by a compression spring 72 for engagement with seat 74 when the coupling parts are disconnected, and movement of the valve to the left is limited by compression of spring 72 against the piston spider shoulder 76. Movement of the spider to the left is limited by engagement with the snap ring 78 located within the booster piston.
- the valve 70 and seat 74 will engage when the coupling parts are separated to prevent entry of foreign matter into the female coupling part.
- the male part 12 is of a conventional construction including a passage 80 internally threaded for receiving the hose fitting 82 associated with the hose 14. Externally, the part 12 includes the conventional ISO annular groove 84 for receiving the locking balls 40, and the cylindrical nose 86 sealingly engages with the sleeve supported seal 88. Internally, the part 12 is provided with a spider 90 slidably supporting the self-sealing valve 92 which is biased toward the left for engagement with the seat 94, Fig. 1, by the compression spring 96. The valve 92 includes a nose 98 extending to the left beyond the left end of the part body.
- the coupling cap 34 preferably includes a pivoted cover 100 for enclosing the open end of the part 10 when the part 12 is uncoupled therefrom.
- the shaft 54 In the uncoupled state, due to the previous release of part 12, the shaft 54 will be pivoted counterclockwise to the position shown in Fig. 1, shifting the sleeve 26 to the right, engaging ball retainer 44 with snap ring 50 aligning the retainer recess 48 with the balls 40.
- the booster piston 64 will be located at its outer position, Fig. 4, and the central valve 70 will be engaging the seat surface 74 under the influence of the spring 72. Also, the passage 16 will be sealed by engagement of the valve 20 with the seat 22 as in Fig. 1.
- the cover 100 is pivoted downwardly to the position of Fig. 1, and the male part 12 inserted into the open end of the sleeve 26.
- the balls 40 will be forced outwardly into the retainer recess 48 by nose 86 permitting the groove 84 to align with the balls and when the male nose is fully inserted into the sleeve, the components will be related as illustrated in Fig. 1.
- valve 92 has unseated valve 70.
- the operator begins to rotate the shaft 54 in a clockwise direction, causing the eccentric pin 60 to shift the sleeve 26 to the left.
- This motion causes the sleeve to move under the retainer 44, Fig. 2, aligning the retainer surface 102 with the balls 40 forcing and holding the balls into a locking relationship with the groove 84.
- the part 12 is moved to the left by the balls and the valve 92 engaging the booster piston valve 70 compresses the spring 72 to shift the booster piston 64 to the left.
- a radial orifice 106 is defined in the sleeve 26 between chamber 104 and the right side of the piston head 28, pressurizing the chamber 36 which imposes a hydraulic force upon the sleeve 26 aiding movement of the sleeve to the left. In this manner the operation of the shaft 54 is hydraulically augmented, and this hydraulic assist will exist as long as the valve 20 is unseated.
- Fig. 3 represents the relationship of the components when the parts 10 and 12 have been fully coupled, and prior to shifting of the booster piston 64 to the right. At this time the sleeve 26 will be engaging the left end of the chamber 36 and the passages within body 10, and booster piston 64 are fully open.
- the chamber 108 "behind" the booster piston head 66 is vented to the atmosphere by radial passage 110 formed in the sleeve, and fluid pressure acting upon the piston head will force the booster piston 64 to the right.
- This movement of the booster piston carries the valve 70 to the right unseating the male self-sealing valve 92 from its seat 94 to establish full flow through the coupling as illustrated in Fig. 4.
- This movement of the booster piston permits the female part valve 20 to return to its normal position as illustrated in Fig. 4, and the coupling is now in its operative condition.
- the hydraulic assisting and balancing of the sleeve movement due to the sleeve piston head 28 permits the coupling of the invention to be easily operated, yet inadvertent sleeve operation is prevented.
- the use of the booster piston 64 to unseat the male self-sealing valve 92 insures that the coupling components will be open regardless of the initial pressure existing within the supplied circuit system and part 12, and operation of the coupling will always properly occur regardless of the pressure conditions within the supply and supplied cicuits.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Quick-Acting Or Multi-Walled Pipe Joints (AREA)
Abstract
Description
- Couplings with self-sealing valves are commonly utilized in fluid circuits to prevent the escape of fluid when the parts are uncoupled. Such self-closing valves are usually spring biased, and are located within the coupling part adjacent the end thereof whereby the valves of the parts engage during coupling to displace each other and open the part passages. Such self-sealing couplings are easily connected if the fluid pressure within a part, or parts, is nil or low, but internal pressure renders coupling of self-sealing parts difficult if the internal fluid pressure must be overcome to displace the valves and permit complete interlocking of the parts.
- Fluid couplings used with agricultural equipment must be readily coupled and uncoupled, self-sealing, and of the "breakaway" type wherein the coupling parts automatically separate when the axial tension in the hose lines reaches a predetermined force, as will happen if the implement being towed by the tractor is inadvertently dehitched, or the hitch trips because the implement strikes an immovable object.
- Also, with agricultural hydraulic systems it is not uncommon for high pressures to exist within the supplied implement circuit wherein fluid pressure is produced by the weight of the implement hydraulically-operated components. In such instances the pressure within the implement circuit renders interlocking of the coupling parts difficult due to the implement pressure and the supply pressure at the tractor.
- Available hydraulic fittings for agricultural systems have not successfully overcome the aforementioned problems, and it-is the purpose of the invention to provide a fluid fitting which is capable of overcoming the aforedescribed situations.
- It is an object of the invention to provide a fluid coupling which is of the "breakaway" type utilizing self-sealing valves but is capable of transmitting and operating at high fluid pressures, and wherein the valves do not inadvertently close or check due to high volume flow.
- Another object of the invention is to provide a fluid coupling wherein the interconnection of the coupling parts is achieved by a manually operated lever, and coupling of the parts is assisted by the hydraulic pressure within the pressurized supply circuit.
- A further object of the invention is to provide a self-sealing fluid coupling utilizing standard interfaces, and wherein interconnection of the parts is hydraulically assisted.
- Yet another object of the invention is to provide a "breakaway" self-sealing fluid coupling wherein the coupling parts each contain self-sealing-valves, and fluid pressure within the supply part is utilized to unseat the self-sealing valve within the supplied part permitting mating and interlocking of the coupling parts regardless of the fluid pressure within the supplied circuit.
- In the practice of the invention the female coupling part is connected to the supply side of the circuit utilizing a pump, while the male coupling part communicates with the supplied circuit. The coupling parts utilize standard interface configurations, and an annular sleeve mounted upon the female part utilizes radially movable balls to connect to the male part and a manually operated lever axially translates the sleeve to draw the male part into the female.
- An expansible chamber motor is defined in the female coupling part communicating with the supplied pressurized fluid during part interconnection to assist in the axial displacement of the sleeve and operation of the lever.
- The self-sealing valve within the female and male coupling parts engage during interconnection, and the female part includes an expansible booster motor in communication with the supplied pressure for displacing the male self-sealing valve if the pressure within the supply circuit is too great to permit the self-sealing valve to open during mech.anical interconnection. This booster motor assures opening of the supplied circuit regardless of the static pressure therein.
- The sleeve may be displaced by the tension within the coupling parts to provide a "breakaway" operation, and the aforementioned structure is concisely incorporated within a coupling configuration and size comparable to available couplings for similar applications.
- The aforementioned objects and advantages of the invention will be appreciated from the following description and accompanying drawings wherein:
- Fig. 1 is an elevational view, partially sectioned, of fluid coupling in accord with the invention, the male part being inserted, but unlocked,
- Fig. 2 is an elevational, partially sectioned view similar to Fig. 1 illustrating lever and sleeve movement sufficient to lock the male part within the female,
- Fig. 3 is an elevational, partially sectioned view showing the fully coupled interrelationship of the parts, but prior to opening of the male self-sealing valve, and
- Fig. 4 is an elevational, partially sectioned view illustrating the booster motor in its operative position opening the male self-sealing valve.
- With reference to the drawings, the coupling
female part 10 is usually hard mounted, such as being attached to the pressurized supply circuit of the tractor or the like. The supplied circuit, such as the circuit of a farm implement, includes themale part 12 mounted upon aflexible hose 14 and connectable to thefemale part 10. - The female part -10 includes a
passage 16 internally threaded at the left to receive a pressurized conduit from the pump, having a tubular sleeve which telescopingly supports thevalve 20 which is biased toward a sealing relationship with the conical seal 22 bycompression spring 24. - An
annular sleeve 26 is mounted upon thecoupling part 10 for axial displacement, and the sleeve includes anannular piston head 28 internally and externally grooved to receivesealing rings 32. Theannular cap 34 mounted upon thepart 10 forms anannular chamber 36 in which thesleeve piston head 28 reciprocates. At its right end, thesleeve 26 is provided with acylindrical portion 38 having a plurality of radially extending circumferentially spaced holes each receiving a radiallymovable ball 40. Asnap ring 42 defined in a groove adjacent the right end of the sleeve limits the movement of theannular ball retainer 44 on thesleeve 26 as biased to the right by thecompression spring 46. Theball retainer 44 includes anannular recess 48 partially defined by an oblique cam surface, and movement of the retainer to the right is limited by engagement with thesnap ring 42, or thesnap ring 50 located within theannular cap 34. A flexibleelastic skirt 52 prevents the entrance of foreign matter. - An
operating shaft 54 is rotatably mounted upon thecap 34 withincylindrical recess 56, and the shaft includes ahandle 58 pinned thereto. At its lower portion the shaft includes an eccentric pin 60 received within the annular groove 62 defined within thesleeve 26 whereby rotation of the shaft by thehandle 58 will axially displace the sleeve upon thecoupling part 10. Spring detent means, not shown, may be utilized to hold theshaft 54 in its open and closed rotary positions upon thecap 34. - A booster piston assembly generally indicated at 64 is located within the passage of the
female part 10, and the booster piston includes ahead 66 sealingly engaging the sleeve by means of an O-ring. Thebooster piston 64 includes an axially extendingportion 68 also sealed to the sleeve and acentral valve 70 is defined in the booster piston engagable withseat 74. Thevalve 70 is biased to the right by acompression spring 72 for engagement withseat 74 when the coupling parts are disconnected, and movement of the valve to the left is limited by compression ofspring 72 against the piston spider shoulder 76. Movement of the spider to the left is limited by engagement with thesnap ring 78 located within the booster piston. As will be noted, thevalve 70 andseat 74 will engage when the coupling parts are separated to prevent entry of foreign matter into the female coupling part. - The
male part 12 is of a conventional construction including apassage 80 internally threaded for receiving the hose fitting 82 associated with thehose 14. Externally, thepart 12 includes the conventional ISOannular groove 84 for receiving thelocking balls 40, and thecylindrical nose 86 sealingly engages with the sleeve supportedseal 88. Internally, thepart 12 is provided with aspider 90 slidably supporting the self-sealingvalve 92 which is biased toward the left for engagement with theseat 94, Fig. 1, by thecompression spring 96. Thevalve 92 includes anose 98 extending to the left beyond the left end of the part body. - The
coupling cap 34 preferably includes apivoted cover 100 for enclosing the open end of thepart 10 when thepart 12 is uncoupled therefrom. - In the uncoupled state, due to the previous release of
part 12, theshaft 54 will be pivoted counterclockwise to the position shown in Fig. 1, shifting thesleeve 26 to the right,engaging ball retainer 44 withsnap ring 50 aligning theretainer recess 48 with theballs 40. Thebooster piston 64 will be located at its outer position, Fig. 4, and thecentral valve 70 will be engaging theseat surface 74 under the influence of thespring 72. Also, thepassage 16 will be sealed by engagement of thevalve 20 with the seat 22 as in Fig. 1. - To couple the
part 12 to thepart 10, thecover 100 is pivoted downwardly to the position of Fig. 1, and themale part 12 inserted into the open end of thesleeve 26. Theballs 40 will be forced outwardly into theretainer recess 48 bynose 86 permitting thegroove 84 to align with the balls and when the male nose is fully inserted into the sleeve, the components will be related as illustrated in Fig. 1. Note thatvalve 92 hasunseated valve 70. - Thereupon, the operator begins to rotate the
shaft 54 in a clockwise direction, causing the eccentric pin 60 to shift thesleeve 26 to the left. This motion causes the sleeve to move under theretainer 44, Fig. 2, aligning theretainer surface 102 with theballs 40 forcing and holding the balls into a locking relationship with thegroove 84. Thepart 12 is moved to the left by the balls and thevalve 92 engaging thebooster piston valve 70 compresses thespring 72 to shift thebooster piston 64 to the left. - As rotation of the
shaft 54 continues by rotation of thehandle 58 thesleeve 26 is moved further to the left causing thevalve 70 to engage the nose of thevalve 20. This action will unseat thevalve 20 from its seat 22, pressurizing thechamber 104 from the pressurized fluid source. - A
radial orifice 106 is defined in thesleeve 26 betweenchamber 104 and the right side of thepiston head 28, pressurizing thechamber 36 which imposes a hydraulic force upon thesleeve 26 aiding movement of the sleeve to the left. In this manner the operation of theshaft 54 is hydraulically augmented, and this hydraulic assist will exist as long as thevalve 20 is unseated. - Fig. 3 represents the relationship of the components when the
parts booster piston 64 to the right. At this time thesleeve 26 will be engaging the left end of thechamber 36 and the passages withinbody 10, andbooster piston 64 are fully open. - The
chamber 108 "behind" thebooster piston head 66 is vented to the atmosphere by radial passage 110 formed in the sleeve, and fluid pressure acting upon the piston head will force thebooster piston 64 to the right. This movement of the booster piston carries thevalve 70 to the right unseating the male self-sealingvalve 92 from itsseat 94 to establish full flow through the coupling as illustrated in Fig. 4. This movement of the booster piston permits thefemale part valve 20 to return to its normal position as illustrated in Fig. 4, and the coupling is now in its operative condition. - It will be appreciated that in the operative position of Fig. 4 the components are so related that even under high capacity fluid flow conditions the valves will not close or check, and inadvertent valve closing is prevented.
- In the event that excessive axial tension to the right is applied to the coupling due to unhitching of the implement, the resultant axial force that is applied to the
sleeve 26 will release the detent associated with theshaft 54, and as the crank is not "on" center with respect to the shaft movement thesleeve 26 will be pulled to the right against the fluid pressure acting on the sleeve at thepiston head 28, and when the sleeve has moved to the position of Fig. l, theretainer 44 will engagering 50 and theballs 40 will be released permitting thecoupling part 12 to be released from thepart 10. This releasing action, of course, closes thevalves - The hydraulic assisting and balancing of the sleeve movement due to the
sleeve piston head 28 permits the coupling of the invention to be easily operated, yet inadvertent sleeve operation is prevented. The use of thebooster piston 64 to unseat the male self-sealingvalve 92 insures that the coupling components will be open regardless of the initial pressure existing within the supplied circuit system andpart 12, and operation of the coupling will always properly occur regardless of the pressure conditions within the supply and supplied cicuits. - As appreciated from the drawings, the use of the sleeve piston and booster piston adds little bulk to the coupling and a sophisticated coupling operation is achieved within a concise configuration.
- It will be appreciated that various modifications to the inventive concepts may be apparent to those skilled in the art without departing from the spirit and scope of the invention.
Claims (9)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US06/591,808 US4540021A (en) | 1984-03-21 | 1984-03-21 | Balanced valve coupling |
US591808 | 1984-03-21 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0156553A1 true EP0156553A1 (en) | 1985-10-02 |
EP0156553B1 EP0156553B1 (en) | 1987-07-01 |
Family
ID=24368032
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP85301538A Expired EP0156553B1 (en) | 1984-03-21 | 1985-03-06 | Balanced valve coupling |
Country Status (4)
Country | Link |
---|---|
US (1) | US4540021A (en) |
EP (1) | EP0156553B1 (en) |
JP (1) | JPS60227094A (en) |
CA (1) | CA1243056A (en) |
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EP0216440A2 (en) * | 1985-09-09 | 1987-04-01 | Aeroquip AG | Power-assisted coupling |
GB2196080A (en) * | 1986-08-27 | 1988-04-20 | Sterling Hydraulic Limited | Pressure coupling |
EP0340879A1 (en) * | 1988-05-05 | 1989-11-08 | Erwin Weh | Pressure-sealed plug coupling |
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FR2559941B1 (en) * | 1984-02-16 | 1986-07-04 | Framatome Sa | NUCLEAR REACTOR OF THE SUB-MODERATE TYPE |
DE3704159A1 (en) * | 1987-02-11 | 1988-08-25 | Aeroquip Gmbh | QUICK RELEASE COUPLING FOR PARTICULAR HYDRAULIC LINES |
EP0365189B1 (en) * | 1988-10-21 | 1995-06-14 | Kabushiki Kaisha Kosmek | Quick-acting coupling |
AU5846194A (en) * | 1992-12-07 | 1994-07-04 | Parker-Hannifin Corporation | Push-to-connect coupler with interlocking three-way valve |
US5464042A (en) * | 1994-04-29 | 1995-11-07 | Aeroquip Corporation | Quick connect air-conditioning coupling |
US6082401A (en) * | 1995-01-06 | 2000-07-04 | Colder Products Company | Low spill high flow quick coupling valve assembly |
JPH11500517A (en) * | 1995-01-06 | 1999-01-12 | コールダー・プロダクツ・カンパニー | Low outflow high flow quick connect valve assembly |
US5566714A (en) * | 1995-05-24 | 1996-10-22 | Applied Power Inc. | Hydraulic coupler |
US6161578A (en) * | 1996-10-09 | 2000-12-19 | Colder Products Company | Low spill high flow quick coupling valve assembly |
US6016835A (en) * | 1998-02-23 | 2000-01-25 | Parker-Hannifin Corporation | Hydraulic quick disconnect coupling |
US5996632A (en) * | 1998-12-14 | 1999-12-07 | Aeroquip Corporation | Pressure relief adapter |
US6158717A (en) * | 2000-04-18 | 2000-12-12 | Perfecting Coupling Company | Quick-action fluid coupling |
US6655656B2 (en) | 2000-11-10 | 2003-12-02 | Parker Hannifan Corporation | Quick disconnect coupling |
ATE366892T1 (en) * | 2002-12-18 | 2007-08-15 | Witt Gmbh & Co Holding Und Han | QUICK CONNECTION COUPLING WITH ACTUATING DEVICE FOR THE TRANSFER OF A GASEOUS AND/OR LIQUID MEDIUM |
US8056581B2 (en) * | 2006-04-06 | 2011-11-15 | Fastest, Inc. | Latching connectors |
JP4986520B2 (en) * | 2006-07-10 | 2012-07-25 | サーパス工業株式会社 | Coupling device for fluid transfer |
KR100784142B1 (en) | 2006-12-22 | 2007-12-10 | 주식회사 포스코 | Coupling |
ITMI20131866A1 (en) | 2013-11-11 | 2015-05-12 | Stucchi Spa | COUPLING WITH FLAT FACE FOR FLUID TRANSMISSION WITH ANULAR FRONT GASKET. |
JP6456067B2 (en) * | 2014-07-30 | 2019-01-23 | 株式会社藤井合金製作所 | Flow path connection device |
US11125479B1 (en) | 2016-09-28 | 2021-09-21 | Joi Holding Llc | Apparatus and process for amateur HVAC installation |
US11982451B1 (en) | 2016-09-28 | 2024-05-14 | Joi Holding Llc | Apparatus and process for amateur HVAC installation |
US20200088417A1 (en) | 2016-09-28 | 2020-03-19 | Jason Ingram | Apparatus and process for amateur ductless hvac installation |
USD1010776S1 (en) | 2017-09-28 | 2024-01-09 | Joi Holding Llc | Female quick-connect connector |
USD1008425S1 (en) | 2017-09-28 | 2023-12-19 | Joi Holding Llc | Male quick-connect connector |
FR3080165B1 (en) * | 2018-04-12 | 2020-05-01 | Staubli Faverges | FITTING ELEMENT AND FITTING COMPRISING SUCH A FITTING ELEMENT |
JP7150310B2 (en) * | 2018-07-27 | 2022-10-11 | サーパス工業株式会社 | FLUID TRANSFER CONNECTOR AND CONTROL METHOD THEREOF |
USD1008426S1 (en) | 2020-04-02 | 2023-12-19 | Joi Holding Llc | Quick-connect coupler |
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CH547981A (en) * | 1970-08-10 | 1974-04-11 | Hansen Mfg Co | PIPE COUPLING. |
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FR2402826A1 (en) * | 1977-09-12 | 1979-04-06 | Gould Inc | LEVER TYPE QUICK DISASSEMBLY FEMALE FITTING |
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USRE23925E (en) * | 1947-09-08 | 1955-01-18 | Coupling | |
US3215161A (en) * | 1962-12-13 | 1965-11-02 | Aeroquip Corp | Self-sealing coupling |
US3291152A (en) * | 1964-01-07 | 1966-12-13 | Thiokol Chemical Corp | Self sealing quick disconnect coupling |
US3348575A (en) * | 1965-08-16 | 1967-10-24 | Int Harvester Co | Hydraulically actuatable fluid coupling |
US3431942A (en) * | 1966-02-23 | 1969-03-11 | Arnold F Kopaska | Hydraulic coupler |
US3646964A (en) * | 1967-02-28 | 1972-03-07 | Parker Hannifin Corp | Coupling device for permitting coupling under trapped pressure |
US3507523A (en) * | 1969-02-25 | 1970-04-21 | Air Lock Inc | Disconnectable coupling for fluid pressure lines |
US3710823A (en) * | 1971-01-25 | 1973-01-16 | Dempco | Hydraulic coupler with cam actuator |
US3730221A (en) * | 1971-07-09 | 1973-05-01 | Dempco | Hydraulic coupler with pressure relief mechanism |
JPS5630693B2 (en) * | 1972-11-06 | 1981-07-16 | ||
US4009729A (en) * | 1975-10-20 | 1977-03-01 | Dempco, Inc. | Hydraulic coupler |
US4213482A (en) * | 1978-10-25 | 1980-07-22 | Gondek John T | Hydraulic coupler |
US4222411A (en) * | 1979-01-19 | 1980-09-16 | Parker-Hannifin Corporation | Lever actuated fluid coupling |
JPS55120885U (en) * | 1979-02-19 | 1980-08-27 | ||
JPS605176Y2 (en) * | 1979-08-16 | 1985-02-16 | 日東工器株式会社 | pipe fittings |
US4303098A (en) * | 1980-04-14 | 1981-12-01 | Deere & Company | Female coupler |
-
1984
- 1984-03-21 US US06/591,808 patent/US4540021A/en not_active Expired - Lifetime
-
1985
- 1985-03-04 CA CA000475693A patent/CA1243056A/en not_active Expired
- 1985-03-06 EP EP85301538A patent/EP0156553B1/en not_active Expired
- 1985-03-19 JP JP60055612A patent/JPS60227094A/en active Granted
Patent Citations (3)
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CH547981A (en) * | 1970-08-10 | 1974-04-11 | Hansen Mfg Co | PIPE COUPLING. |
US4074698A (en) * | 1976-07-26 | 1978-02-21 | Seymour Manufacturing Co., Inc. | Hydraulic coupler |
FR2402826A1 (en) * | 1977-09-12 | 1979-04-06 | Gould Inc | LEVER TYPE QUICK DISASSEMBLY FEMALE FITTING |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0216440A2 (en) * | 1985-09-09 | 1987-04-01 | Aeroquip AG | Power-assisted coupling |
EP0216440A3 (en) * | 1985-09-09 | 1987-10-14 | Aeroquip Ag | Power-assisted coupling |
GB2196080A (en) * | 1986-08-27 | 1988-04-20 | Sterling Hydraulic Limited | Pressure coupling |
EP0340879A1 (en) * | 1988-05-05 | 1989-11-08 | Erwin Weh | Pressure-sealed plug coupling |
WO1989011059A1 (en) * | 1988-05-05 | 1989-11-16 | Erwin Weh | Pressure-sealed plug coupling |
Also Published As
Publication number | Publication date |
---|---|
EP0156553B1 (en) | 1987-07-01 |
JPS60227094A (en) | 1985-11-12 |
US4540021A (en) | 1985-09-10 |
JPH0232518B2 (en) | 1990-07-20 |
CA1243056A (en) | 1988-10-11 |
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